Internal combustion motor



Sept. 24, 1963 c. l. GESELI. 3,104,527

INTERNAL coMBusToN MOTOR CAR/.0S l. 6E $5 LL ATTORNEYS' c. l. GESLL 3,104,527

sept. 24, 1963 INTERNAL COMBUSTION MOTOR 5 Sheets-Sheet 2 Filed Nov. 13, 1961 Zic 76e 8c INVENTOR CARLOS L 6E' 5E Ll.

BY M

ATTORNEYS Sept. 24, 1963 c. l. GEsELL INTERNAL coMBusTIoN MOTOR Filed Nov. 13. 1961 5 Sheets-Sheet 3 INVENTOR GARLOS l. GESELL ATTORNEYS Sept. 24, 1963 c. l. GEsELl.

INTERNAL coMBUsTzcoN MoToR 5 Sheets-Sheet 4 Filed Nov. 13, 1961 INVENTOR CARLOS GESELL BY M ATTORNEYS Sept. 24, 1963 c. 1. GEsELl. 3,104,527

INTERNAL coMBUsTIoN MOTOR Filed'Nov. 13, 1961 5 Sheets-Sheet 5 (P=20K CM2) P=2O FACTOR O O P=\5 'FACTOR i roo CENTER oF P=\o FACTOR ROTARY MEMBER \6 5 CENTER oF \oo l ROTARY MEMBER 2l (4) P=6 FACTOR IOO P=3 l FACTOR INVENTOR CARLOS l. GESELL ATTORNEYS United States Patent O 3,104,527 INTERNAL (Jlt/IBUSTIN MOTOR Carlos I. Gesell, iia Gesell, Via Iuancho, ENGR., Argentina Filed Nov. 13, 1%1, Ser. No. 151,759 21 Claims. (Cl. 60-39.63)

This invention relates to improvements in rotary apparatus involving compression and expansion of gases and action thereto and resulting therefrom.

An object of the invention is to provide rotary apparatus having expansible chambers therein providing for `action on and by gases.

Another object of the invention is to provide rotary power `developing apparatus utilizing fuel and air in a more efficient manner than in conventional engines.

A further object is to provide for more efficient and complete burning of fuel supply in engines so as to eliminate poisonous exhaust gases.

A still further object of the invention is to provide a rotary power developing apparatus tha-t may successfully work at much higher rotational speeds without affecting the required time of combustion in a combustion chamber apart from the rotary parts of power developing gases while they are maintained at maximum pressure.

Another object of the invention is to provide a rotary power developing engine that may be efficiently cooled by air.

A further object of the invention is to provide a type of rotary power gas engine that Irnay be equally as well designed for use in generating power in a large power plant of any size.

A still further object -is to provide a combustion engine that will work with practically any fuel, not requiring anti-knock compounds thereby eliminating other sources of air pollution.

These together with other objects and advantages which bec-ome subsequently apparent reside in the details of construction and operation as more fully hereinafter described and claimed, reference being had to the accompanying drawings forming a part hereof, wherein like numerals refer to like parts throughout, and in which:

FIG. l is a plan view of the engine;

FIG. 2 is a front elevation of the engine of FIG. l;

FIG. 3 is a sectional view along line 3-'3 in FIG. 2;

FIG. 4 is a fragmentary sectional side elevation of the manifold plate and its mounting on an enlarged scale;

FIG. 5 is a sectional view along line 5 5 of FIG. 2 showing the engine per se on an enlarged scale;

FIG. 6 is a sectional view along line 6-6 of FIG. 5 but with the combustion chamber shown in full;

FIG. 7 is a cross-sectional view of -the manifold plate showing the relationship of the passages therein;

FIG. 8 is a fragmentary sectional view on line 8 8 in FIG. 6 showing the anti-friction roller and its guide on an enlarged scale;

FIG. 9 is a perspective view of one of the piston-like members with tguide rods for the member and guide means and mounting of the anti-friction roller on an enlarged scale;

FIG. 10 is `a cross-sectional view on an enlarged scale of the external combustion chamber shown in FIG. 6;

FIG. 11 is a cross-sectional view of the external cornbustion chamber along line 11-11 of FIG. l0;

FIG. l2 is a fragmentary side elevation partially in section of the rotary apparatus with a modified type of anti-friction means between piston-like member and outer surrounding member;

FIG. 13 is a perspective view showing the modified piston-like member and its modified anti-friction means in the form of a sphere;

Patented Sept. 24, 1963 ice FIG. 14 is a sectional view along line 145-14 of FIG. l2 on an enlarged scale showing the piston-like member in its cylinder with a spherical anti-friction means; and

FIG. l5 is a diagrammatic showing of a force diagram illustrative to some extent of the working forces on the power half of one revolution.

The rotary power engine is generally indicated at 1t) and a bedplaite 11 is provided for mounting the various parts. Extending up from the bedplate 1l are integrally oast or otherwise attached spaced a-pabt standards 12. and 13. Standard 12 has a thrust bearing 14 at its upper end with a bearing `cap 14a and securing cap screws Mb. The upper portion of standard 13 has an offset and vertically extending mounting portion 13a adjacent a bearing 1S thereon which has `a bearing cap 15a and securing cap screws 15b. This bearing 15 may also be a thrust bearing like bearing 14 for the shaft 16a received therein.

Reference to FIGS. 1, 2 and 6 shows a first rotary member 16 having an axle 16a extending transversely to one side thereof and received in bearings 14a and 15a. A suitable power delivery pulley or gear 1612 may be attached .to the shaft 16a. The first rotary member has a plurality of radially extending equally spaced apart cylinder members 17 formed therein or attached thereto and these are provided with suitable air cooling `fins 17a as representatively shown on one cylinder in FIG. 5. The cylinders have an inner end 17b and an outer open end 17C. In the hub portion 16C of the first rotary member 16 there is formed for each cylinder a first supply air passage 16e extending from the inner end 17h of cylinder 17 to an outer face 16d on the first rotary member and in like manner but further in toward the center of the hub 16C there is formed a first exhaust passage 16j. Both of these passages 16e and 161 are relatively short and each for each cylinder terminates in face 16d so as to uniformly lie within a circular path for each of such passageways as shown in FIG. 5.

Adjacent each cylinderv member 117 is a pair of oppositely disposed elongated cavities 17d which extend parallel to the radial axis of their cylinder thereadjacent.

Mounted in each cylinder 17 is a piston-like member '1S closed at each end and provided with suitable piston rings 18a. When anti-friction rollers 19 are used between the ends of the pistons and the surrounding rotary member means must be provided to prevent rotation of the piston about their axis so that the rollers will not bind. Gppositely positioned transversely extending ears 1gb are attached adjacent the outer end portion of each piston and to these ears there are attached guide rods I18C which extend parallel to the axis of the piston and spaced oppositely therealong so as to be reciprocably received within the cooperating elongated cavities 17e ofthe cylinder 17. The fit of the vguide rods 18C in the cavities 17C is such that littleV resistance to reciprocating movement of the piston is present. Mounted on the end of each piston 1S is an anti-friction cylindrical roller 19 which has free abutting contact with the adjacent outer closed end `18d of piston 1S so that pressure acting on piston 18 moving it outward is throught against the roller 19. In order to maintain the roller 19 oriented, there is provided a guide mounting 20, see FIG. 9, on the piston 18. This guide mounting may be variously constructed )but as here shown there are provided spaced apart mounting posts Zita, two spaced apart adjacent each end of 'roller 19 and having secured therebetween a guide plate 20h as by screws 20c. A longitudinally extending slot 25d extends in guide plate 2Gb and receives an end guide pin 19a in roller 19 in a free rolling manner which does not interfere with the roller 19 taking up pressure imposed by the end 18d of piston 18 and transferring it to the outer surrounding member to -be described while the roller '19 rolls towards one end then the other end of the guide slot 20d in each guide plate 28h, once every rotation of the rotary members 16 and 21 rotating together.' A modified form of anti-friction means utilizing a sphere instead of a roller is shown later.

A second rotary member or camming gear is generally indicated at 21 having an axle 21a extending transversely therefrom in opposite position to axle 16a of the lirst rotary member received within this second rotary member. Supporting rotary member 21 is a pair of spaced apart vertically extending standards 22 and 23 attached to bedplate 11 on the opposite end thereof from standards 12 and 13 and secured to bedplate 11 'by cap screws 22a and 23a or cast integrally therewith. Suitable bearings are supported in the upper ends of standards 22 and 23- to rotatably mount shaft 21a and suitable bearing caps 22b and 23h hold the shaft 21a in the bearings and these caps are secured by cap screws 22C and 23C respectively. These bearings may be suitable thrust bearings which may receive the shaft 21a therein which may be provided with a collar portion thereon to cooperate with the thrust bearing. The bearings supporting shaft 21a are at a higher level than the bearings supporting shaft 16a of the first rotary member and thus the second rotary member 21 receives the tirst rotary member 16 in oiset relationship whereupon, as best shown in FIGS. and 6, these two rotary members are eccentrically mounted for rotation together.

The second rotary member 21 is here illustrated as having an end disc portion 2lb integral with shaft 21a and extending in spaced relationship alongside rotary member 16 and having integrally therewith and extending transversely from its periphery a circular backup wall or ring 21C that serves as a pressure receiver bearing member for rollers 19 which roll to and fro along the inside adjacent periphery 21d thereof. An annular cover plate 24 is received by the well 21C and secured thereto by Screws 24a.

As shown by the arrows cooling air from the cylinders 17 is sucked in through a plurality of parts 21e in disc portion 2lb adjacent axle 21a of the second rotary member and through spaced apart apertures 24h in cover plate 24 and forced over the external fins 17a on the cylinders 17 and ung outwardly through vent apertures 21e in the circular backup wall 21C spaced in circular rows to each side of the bearing surface therein for rollers 19.

An annular manifold plate 25 is received over axle 16a and adjacent face '16d of the first rotary member 16 and in spaced annular relationship to the annular cover plate 24 on the second rotary member 21. The manifold plate 2S is mounted for slight axial movement to permit the breaking of compression in the engine for starting. The manifold plate 25 is shown mounted on the offset vertical top portion 13a of standard 13 in FIGS. l, 2 and 4 and on shaft 16a. Manifold plate 25 has a transversely extending integral hollow hub portion 25a received over axle 16a and within a recess 13b in portion 13a of the standard 13. A suitable rack 2517 is formed on hub portion 25a and it meshes with a pinion gear 26 disposed in a cavity 13C and fixedly mounted on a shaft 26a suitably rotatably supported in standard portion 13a. Shaft 26a has aiiixed to one end an operating lever 2Gb. The manifold plate 25 has guide pins 25e aixed to its back-face and received within recesses 13a' in standard portion 13a. Suitable compressionV springs 25d are received by the pins 25C and disposed between the back of manifold plate 25 and standard portion 13a to bias the manifold plate into engagement lwith the face 16d of rotary member 16. The bearing surface of the manifold member 25 ymay have an anti-friction coating thereon, such as Teflon as indicated at 25e.

The manifold plate 25 has for-med thereinV a supply lair passage 25e which communicates 'with an 'arcuate passageway 25e formed in the bearing face thereof of a sufficient length lthat the air may readily be transferred. Here the transfer station for cyclic alignment is shown las a first sta-tion I, see FIGS. 5 and 6. This first station I is at a position in the engine where the expansible chamber formed within each cylinder-17 is approximately greatest. Positioned approximately diametricalfly from this first sta- 25f which extends through the plate Iand terminates Vin an arcuate passageway portion 25f extending yas here illustratively shown an arcuate distance equal to at Ileast the arcuate distance bet-Ween two adjacent lirst exhaust passageways 116jt land for cyclic communication therewith, Where increased working pressures are used the length of this passage may be decreased. As shown in FIGS.

5 and 7, for illustration, these passageway portionsV 25e' and 25]" may extend to accommodate partially simultaneously two or more adjacent cylinders in a cyclic manner as the first rotary member 16 and the second rotary member 21 rotate together to give the scavenging an ample opportunity to soavenge out fthe gases of the previous cycle and to retard the lbeg-inning of compression.

At the second station II positioned approximately diametricaliy opposite the first station I there is provided in manifold plate 2S a compressed air supply passageway 25g extending therethrough to the backside of the manifold plate 'and communicating Iwith an arcuate passageway or channel as to be in alignment with the first supply :air passageway 15e in the first rotary member in a cyclic manner so as to receive the `compressed supply air Itherethrough and conduct it to a combustion fold plate 25. A combustion gas passageway 25h is positioned i-n plate 25 at the second-station IIA arcuately spaced from the passageway 25g in the direction of rotation of the engine and terminates in way/portion 25h 'which is in arcuate alignment with `arcuate passageway portion 25g and supply air passageway 16e in the first rotary member for each cylinder in a cyclic manner. This arcuate passageway 25h extends a distance so as to arc to give sufficient time in the rotation for a convenient transfer of gases to the expansible chambers as they pass station Il. This greater distance or span of entry is necessary over that of `the compressed air supply outlet as there is 1a greater volume of gas to transfer. bustion gas passageways 25h and 25h `communicate with the exhaust conduit fromthe `combustion chamber 27 so as to provide a path for Iconducting gases to lthe expansible chambers.

The manifold plate 25 with its passages and the passages in the first rotary member 16 in elect form sliding valves at the stations I and II.

In FIGS. l0 and l1 the combustion chamber 27, as

illustrative for .a combustion engine, is shown to be generallycylindrical in shape having Ian inner cylindrical high temperature casinfgrZ'tz with insulation 27b thereabout and lan outer cylindrical enclosing casing 27C which is secured to manifold plate 25 as by lugs 27d. Within the combustion chamber 27 is made of suitable high temperature resistance material and Supported by webs 29 extending to rthe inner casing 27a. A fuel nozzle 30 extends through the combustion chamber Iwalls and just through Ithe rear wall 28a of the A conduit 31 connects theV v compressedrsupply air passage conical-like shaped member.

25g in plate 25 to the combustion chamber. Within theV conduit 31 is ya compressed air supply conduit which leads from within conduit 31 to the rear portion of the conical member 28 adjacent the fuel supply nozzle opening 36a. Thus, there is formed two streams of compressed air supply, one to the conical member 23 and one to surround the conical member 28 whereupon the burned fuel gas in 28 which portion 25g inthe front face thereof so chamber 27 mounted on yInanian arcuate pass-agespan a sufficient number of degress of These com-y a cone shaped member 28V has perforations Sb therein mix with the surrounding stream of compressed air supply to increase the volume and lower the temperature somewhat. The `air supplied within the conical member 2S where combustion takes place is sutllcient for complete combustion of the fuel lat relatively high temperature. The `air supplied outside the conical member ZS lowers the temperature of the combining combustion gases and compressed yair thereabout within limits -md permits free lrunning of the rotary parts without special cooling. The mixed combustion vgas and compressed air leave the combustion charnber at its end opposite to the nozzle end through conduit 32 4which communicates with lthe combustion gas passageway 25h in plate 25'.

While a combustion chamber has been shown at 27, this could be a heat exchanger device to act thermally on gases. In internal combustion devices, the ygases are heated. ln internal combustion devices, the gases are heated. ln case of use of the apparatus las a refrigeration medium, the compressed gases would here be cooled.

A suitable `electric resistance igniter is generally indicated at 33 with a hot resistance wire portion positioned in adjacent spaced position in fron-t of the fuel nozzle discharge Sila. Suitable insulat'aion members and fittings support the resistance wire and electric leads 33a and 331'; to an electrical power supply (not shown).

Machines of this general nature have been devised by others but with the combustion or thermal chamber within the central part of the cylinder block whereby many complications farise. Bearing means of relatively tremendous size are required.. With the very high temperatures, the matter of expansion and contraction is a major problem with such interior location of thermal `chamber and it is this that has been eliminated in a two rotary member aparatus with eccentric axes of rotation. ln such a type of aparatos, the thermal chamber has been located outside according to this invention. This thus permits use of axles for each rotary member yand of smaller bearings. The difficulties of expansion and contraction and resulting leaks `and sticking is eliminated.

The location of the thermal chamber outside of the rotary members `and the compression-expansion chambers according to this invention has the further advantage that it makes possible the use of -a sliding valve means which is on an exterior portion of the rotary member carrying the cylinders to control the flow of lgases to land from the compression-expansion chambers and the exteriorly positioned thermal chamber. Thus, positive pressure means may be employed to engage the sliding valve tmeans to permit starting and to prevent leakage of `gases yet Leased rotating movement is fully maintained.

A fuel oil pump 34 is mounted on standard i3 and driven by power shaft 16a to supply fuel under pressure. A regulator valve for the fuel supply is indicated at 34a and it is connected by .a high pressure flexible conduit 3d!) to nozzle 30.

An air circulator 35 of the blower type is mounted on bedplate 1l and driven by power shaft 16a of the engine `and takes in air in intake and discharges it under small pressure through a conduit 35h connected to air supply passage 25e in plate 25 through `sli-p joint 35C.

Lubrication may be provided by ra lubrication reservoir 36 mounted on the supply air duct 35h to introduce lubricant. This lubricant becomes vaporized and passes through the various passages and lubricates the moving parts. A iixed shroud 37 is shown in FIG. 3 for illustrative purposes, covering the outer or second rotary member 2l in spaced relation thereto but not preventing exhausting of .the 4Ventilating air. The shroud 37 serves to trap any lubricant being exhausted and baffles it to a suitable sump 37a from where it is picked up by a suitable circulating pump 38 which discharges through a conduit (not shown) to the lubricator 36.

ixedly mounted on the shaft lea `of the iirst rotary 6 member le lis a gear 39 intermediate bearing member 14 and drive pulley leb. The lubrication pump 3S is shown having a drive pinion 3&1 meshing with gear 39.

An electric powered starter motor 49 having la built-in conventional starter clutch mechanism (not shown) drives =a starter pinion 4tlg to star-t the rotary power device.

ln FIGS. l2, l-3 and 14 there is shown la modied type ot anti-friction means for each of the pistons. The cylinders d@ here shown extend outwardly 'a' little further than the Icylinders l? in FlG. 5. Pistons 42. are formed with suitable recesses to receive conventional sealing rings 42a and they are closed at their inner'and outer ends. At the outer end of piston d2 there is a threaded shoulder portion 42h that receives an end cap t3 having a transverse strong botto-m 43a having Ia threaded shoulder received on the threaded shoulder 42h of the piston. The cap i3 has integrally Aformed thereon `a protruding annular shoulder 43e in line with the wall of piston 42 and received within the surrounding cylinder 4l. This end cap i3 and the annular shoulder 43e thereon form a guide means for the yantifriction hardened sphere d4 received therein to transfer thrust of piston 4?. through the bottom 43a of its end cap 43 to the outer surrounding -inner bearing surface Zld of the second rotary 'member 2l.

A large number of rotatable type multicylinder engines have been proposed `which partake of lubrication diiculties in connecting members between the piston :and the pressure backup members due to centrifugal force. Such force at t-he high operating speeds Ithrows the lubrication from the sliding surfaces. Thus, the replacement of the normal connecting means between piston and backup member by one single relatively loose large sphere within means to retain it in lposition on top` of the piston or piston-like member relieves these deiiciencie By this means the difficulty encountered 'with lubrication is obviated as no lubrication is required for the to and fro movement of the relatively free-rolling roller 19 or rolling sphere d4.

ln FlG. l5 there is diagrammatically shown as an approximation lthe rotational forces developed on the one half power revolution as takes place from station Il where combustion gases are introduced. The tangential force larrows at assumed positions l, 2, 3, 4 and 5 are the forces imparting rotation to the rotary device when gases of combustion lare introduced at station ll and impart work through about one-half a revolution and exhaust at station I after performing their work. A brief analysis of the power `developed is given below for the approximation developed in llG. l5.

To find out graphically the torque of rotation at eaoh point: f

(l) Draw a radius line from center of member i6 corresponding to the axis `of reach piston.

(2) Draw a parallel line from center of member 2l.

The relation of length of radius of rotary member 16 to .perpendicular distance separating the two lines multiplied by the gas pressure on the piston gives the torque on the circumference of rotary member 21.

Mode of Operation as a Power Developing Apparatus To start the engine, the manifold plate 2S is raised a slight amount by its operating mechanism so as to reduce the compression and permit the electric starting motor 4t) Y' to drive the rst rotary member 16 in a clockwise direction as viewed in FlGS. 5 and l2. 'Ilhe centrifugal forces drive the pistons 13 and the anti-friction rollers 19, see FIG. 5, outward towards the surrounding wall of the second rotary member 2l to cause it to rotate with rotary member le. The rotation of the two rotary members le and 2l about the two different centers of rotation, see axis of respective axles 16a and 21a, causes the pistons to move within their respective cylinders 17 and the auxiliaries driven by axle 16a to rotate. Included in the auxiliaries is the blower 35 to supply air.

When the desired speed of rotation by the starter motor is reached, the manifold plate 25 is allowed to assume its working position as shown in FIG. 6. The cylinders start to work and provide the rocking motion of the antifriction rollers 19 or spheres 43 and the resulting rotation together of the rotary members i6 and 21.

At station I, supply air is taken from the blower 35 in through passages .25e and 16e to the cyclically adjacent expansible chamber in the cylinder 17. The scavenging air from the blower, i.e. the supply air exhausts the gases from cylinder 17 through passage lef and 25f to the atmosphere in the case of combustion gases. As the cylinders 17 at marked portions A and B in FIG. 5 rotate the passages 16e and 161 thereto cyclically match respectively with the manifold passages 25e' and 25)" in the face thereof. The entrapped supply air in the expansi'ole chamber in cylinder 17 is compressed as at marked positions C-D-E-F. Before the cylinder that has just left the position F gets to the position G, the cylinder is in communication with the combustion chamber 27 whereupon the transfer of the compressed supply air starts and terminates with the cylinder reaching the position G when the whole content of compressed air supply of the charge .is transferred to the combustion or burning chamber 2'7.

In the combustion chamber 27 the current of compressed air is separated into at least two streams, the first stream passes through conduit 2gb to adjacent the nozzle Si) to supply air for combustion of the fuel. The other stream passes through conduit 3i to the chamber 27 and outside the burner 28. The fuel and air are ignited initially by the hot wire igniter 33 and a very high temperature is formed in the gases of combustion within heat resisting conical member 28. When the combustion is complete,

the second part or stream supply of compressed air sup-v ply mixes with the burned gases and partakes their heat and the volume of the combined gases is enlarged, the pressure remaining constant and the temperature correspondingly is lowered. The gases resulting are prepared Working gases and are at the same pressure as at the moment they left the cylinder 17 but have a volume several times as great. These Working gases are conducted through the conduits, passages and ducts provided that are of proper size and positioning to the cylinder 1'7 at positions H, -I and toward i, as may be necessary, through the arcuate passage or channel 2511 in the face of manifold plate 25. As the rotation takes place the access passages close and the work gases expand the expansible chambers and a tangential component of force develops at each cylinder to cause rotation of the rotary members 16 and 21. Such typical tangential forces are shown illustratively in the force diagram in FIG. l5. e

Upon reaching the position, the passages 16e and 16f of the cylinders are cyclically connected to the air supply and exhaust passages 25e and 251 respectively and scavenging air is forced in by the blower and an air supply is taken into the respective cylinders and a new cycle begins. It is important to note that the compression starts at the position C and the expansion linishes at the position A by which it is made clear that the Volume of gases at the beginning of the compression is smaller than the volume of the gases in the expansible chamber at the end of the expansion therein.

it is to be noted that according totheoretical thermodynamics, the addition of more supply air than required for combustion lowers the theoretical eiciency of the cycle, but there is an important factor that oisets these disadvantages related to the heat transfer of the hot gases to the walls in conventional internal combustion engines. -In these referred to conventional engines the gradient of temperature of the walls to the gas is very great and the heat loss is not only proportional to their gradient, but is much more because of the higher thermal conductibility of gases at Ihigh temperatures.

While the combustion chamber 27 is shown mounted as a relatively stationary member outside the expansible chambers, it could be mounted on one of the rotary memcompounds which are extensively used today. These exe haust gases as of today pollute the atmosphere of our cities and adversely affect the health of the population.

II. This apparatus when used as a power developing engine will produce more power with the same quantity of fuel than conventional internal combustion engines because:

(a) The combustion is complete.

(b) The heat losses of the lgases to lthe walls of the cylinders are greatly reduced because:

(l) The engine `according t-o this invention works at' a very high speed, there being no time for heat transfer. This high speed does not interfere with the-time required for complete combustion which takes place Within a well insulated combustion chamber with insulated hot walls, where there is only very little heat loss.

2) The engine `according to `this invention works with a lower temperature of the gases which produces a gain since the difference of :temperatures are less and because the coetlicient of thermal conductivity of the gases at' lower temperatures is less. y (c) The engine according to this invention permits-a higher ratio of compression than conventional explosion engines because there is no possibility of knocking. p

(d) This engine permits complete expansion, or as far as the expansion is desired.

(e) in this machine the combustion is completed at moments of highest pressure. I

(gf) The mechanical eiciency is greater because there are very few parts that cause friction. The pistons whichA in conventional machines are the cause of the greatest friction will cause very little friction in this machine because the :side thrust produced by the connecting rod is less in the herein described machine.

(g) Any type of liquid fuel may be used thus makingy the machine less dangerous which is of special interestl for aircraft and more economical.

(h) This machine is not restricted to a predetermined composition of the air-fuel mixture. The regulation of the speed is obtained by regulating the fuel supply,.it is not restricted to an exact mixture. This makes the machine more foolproof and economical during low power output.

III. This machine may reach much higher speeds of rotation than conventional machines because the speed limiting factor, lthe time required for combustion, takes' place within a chamber separated from the expansible chambers of the engine cylinders, and this explains the cause of the further gains:

(a) Smallness of space required.

(b) Lightness for aircraft.

(c) Reduction `in installation cost because it causes no vibration.

IV. The machine according to this invention is of simple and reliable design and will be of little costin manufacturing because:

(a) It is small and consists of very few parts.

(b) Air cooling is suiiicient and no water with its complications is required.

(c) Complicated and costly carburetors are replaced by simple nozzles. Y Y

(d) The Vcomplicated and costly Iignition devices are of Weight making the machine suitable reduced to igniting the flame at the beginning with an electrically heated wire.

V. This machine gives a practical design for rotary engines to overcome their troubles with valves and bearings.

i claim as my invention:

l. A rotary cylinder power unit including in combination: an air blowing means, a rotatable shaft with beaning and support means, a block fixed thereto to rotate therewith, a plurality of cylinders located in said rotatable block having their open ends extending radially outward and forming compression-expansion chambers for the air from said blowing means, free moving pistons slidable in said cylinders, a camming gear having means for mounting it for backing up forces and pressures from said pistons and for rotation about an axis parallel .to but displaced from said shaft whereupon rotation 4of said gear and said shaft causes a cyclic variation of distance from each of said cylinders to said camming gear, said pistons, upon rotation, exerting thrust against said camming gear due to centrifugal force added to the pressure of the gases causing the pistons Ato make an outgoing movement within the cylinders against the camming gear thereby affecting the pressure of the air er1- closed in the corresponding compression-expansion chambers, relatively free-rolling, antifriction sphere means between said free-moving pistons and said rotatable camming gear whereby forces and pressure are transferred between the piston and camming gear causing a torque eect upon the shaft, means for maintaining in place said sphere means whereby to allow the necessary movement due to eccentricity of the rotating bodies, a stationary combustion chamber having fuel supply means thereto, sliding valve means partly located on said rotatable cylinder block and partly fixed in a non-rotatable fashion to support means, their sliding surfaces closely abutting by pressure means pressing the faces to one another for tightness, both parts provided with duct leans which upon registering cyclically and successively connect two points, firstly said compression-expansion chambers to the blower means when their voltmie is greatest, secondly, said compression-expansion chamber to said combustion chamber when their enclosed space is becoming smallest, thirdly, said combustion chamber back to said compression-expansion chambers when these are beginning to enlarge and inmly said chambers to an exhaust when these compression-expansion chambers have reached their greatest volume, during this last phase the air from the blower scavenging out the used gases and filling in a new charge of fresh air.

2. A rotary power unit according to claim l wherein said spheres are hollow.

3. A rotary power unit according to claim l wherein said duct means has portions thereof providing means for `delaying starting of the compression in said compression-expansion chambers until after part of the movement of the compression stroke has taken place.

4. A rotary power unit according to claim l wherein said air blowing means is drivingly connected to said rst rotatable shaft.

5. A rotary power unit according to claim l wherein sm'd combustion chamber has means associated therewith for rapidly mingling relatively large volumes of excess air over that necessary for complete combustion of said fuel whereby to reduce the temperature of the resulting working gases and enlarge their volume.

6. A rotary power unit comprising in combination: a rotor having an `outside lateral face `and rotatable about an axis and carrying a plurality of cavities in its periphery, said cavities having their outer ends open, pistonlike members received in and forming with said cavities compression-expansion chambers therein, a means rotatable about an axis parallel to and displaced radially from said axis for the rotor, said rotatable means cooperating with said piston-like members to produce a torque effect to rotate the rotor, ducts connecting said compressionexpansion chambers to said outside lateral face of rthe rotor, a stationary member having ducts therein cooperating ywith said lateral face of the rotor to form a sliding valve means, -means to press the parts of the sliding valve means together for tightness, an air Iblowing means and a duct connecting the blower discharge to said stationary member of said sliding val-ve means at a point where the compression-expansion chambers have cyclically their greatest volume, a combustion chamber exterior of said roto-r and the rotatable means cooperating therewith and having entrance and discharge portions, a fuel supply means connected to said combustion chamber for spraying fuel within the combustion chamber, said combustion chamber having mixing means t-o mix large quantities of compressed excess air with said fuel to rapidly and efficiently carry out the mixing within a relatively small space to lower the temperature of the thereby produced Working .gases to be within a range that the employed materials for the compression-expansion chambers will stand and yto enlarge the volume of the working gases and therewith enhance the production of power, a duct connecting the-stationary member of said sliding yalye means and the entrance portion of said combustion chamber at the place where the compression-expansion chambers are becoming cyclically smallest and another duct connecting the combustion chamber at the dischange portion thereof back to the stationary member of the sliding valve means at a point where the compressionexpansion chambers yare beginning to cyclically enlarge again and an exhaust duct means connected to lthe stationary member of said sliding valve means where the compression-expansion chambers have their cyclically greatest volume to discharge expanded exhaust gases exterior of said stationary member of the sliding valve means.

7. A rotary power unit according to claim 6 including means connected to said sliding valve means for movin-g a part thereof axially Ifor venting the compression-expansi-on chambers during starting the said rotary power unit.

8. A rotary power `developing apparatus comprising support means, a first rotary member rotatable about an axis of rotation extending through said support means, a second :rotary member receiving said first rotary member and rotatable about an axis of rotation extending in said support means parallel to said first taxis but displaced therefrom, bearing support means in said rst mentioned support means for supporting said rotary members whereby said first and second rotary members rotate eccentrically ywith respect to each other, said iirst :rotary member having generally radially extending cylinder members thereon, piston-like members received in said cylinders and at their outer end movably exterting thrust against the inside adjacent surfaces of said surrounding second rotary member, said first rotary member having therein for each cylinder first supply and second exhaust passages leading yfrom one face of said first rotary member to the inner end of each cylinder member, said cylinders forming therein expansible chambers between their inner end and the inner end of said pistonlilre members due to the eccentricity of said first and second rotary members as the rotary members rotate together whereby the volume of sa-id chambers is cyclically reduced and enlarged, a manifold plate having a front face thereof slidably abutting said one face of said first rotary member, :means supporting said manifold plate .adjacent said rst rotary member and in nonrctary position with respect to said first rotary member, said manifold plate havin-g `a first lstation and a second station, diemetrically positioned therefrom, said rst st-ation of the manifold plate being positioned approximately adjacent a position wit-h respect to said first and second rotary members where the expansible chamber in said respective cylinders is cyclically greatest, said manifold plate at said first station thereof having an air supply passageway ,and 'an exhaust passageway therethrough for cyclic communication with the respective first supply passage and exhaust passage of each cylinder 'and said manifold plate having in a face thereof passageways connected respectively with the respective supply rand exhaust pass-ageways in the plate and extending to span a distance covering suiicient degrees of arc to enable `full scavenging out of the utilized gases and replacement by an excess new charge of fresh air, a stationary combustion chamber external yof said expansible chambers, said manifold plate -at said second sta-tion thereof having a first passageway in a face 4thereof for cyclic communication with at least one of said passages leading to said cylinders and a connecting passageway therethrough, conduit means connecting said last mentioned passageway in said plate with said combustion chamber to conduct compressed supply air thereto, a fuel supply means f-or supplying fuel to said combustion chamber, a second passageway in the manifold plate at -said second station and 4spaced apart from said first conduit means in the direction of rotation of said first and second rotary members for cyclically communicating with ends of at least one of said passages leading t-o said cylinders and extending to span a distance covering sucient degrees of arc t-o enable full loading of the cylinders cyclically in communication therewith, and a second passage through said manifold plate in communication with said last mentioned passageway, lconduit means connecting said combustion chamber and said second passageway through the plate at the second station whereby combustion gases are cyclically introduced into said cylinders at the second station Iand expand therein causing enlargement of said expansible chambers therein :to impart rot-ation to said first and second rotary members together, said cylinders on cyclically reach-ing said first station giving up their expanded gases and taking in a new charge of supply air an-d means attached to said manifold plate for moving it generally axially `from and to engagement with said first rotary member to interrupt the compression therein for start-ing said apparatus.

9. A rotary power developing apparatus according to claim 8 including means at the first station communieating with the first supply yair passage and the second exhaust passage in said first rotary member for each cylirider to start 'the :compression of supply air in said cylinders lwhen the volume of the expansible chamber therein has reached an amount whereby the volume of the trapped air at beginning of the compression therein is substantially smaller than the volume of such expansible cylinder at the moment of its exhausting at sai-d first station.

l0. A rotary power apparatus according to claim 8 wherein said combustion chamber has means associated therewith for receiving said compressed supply air and separating it into at least two streams and conducting one of said streams to adjacent said fuel fed to said combustion chamber for burning said fuel and wherein the remaining stream or streams o-f Iair within .the chamber acts t-o enlarge the volume of working gases resulting from said burned fuel and to reduce their temperature.

l1. A rotary power developing apparatus according to claim 8 including anti-friction means bearing against the outer end of said piston-like members 4and bearing against the inside adjacent surfaces of said surrounding second rotary member.

12. A rotary power developing apparatus `according to claim 8 including an air circulating means drivingly connected to one of said rotary members to furnish the supply air to said firststation.

13. A rotary power developing apparatus comprising in combination a first rotary member having a supporting axle, a second rotary member receiving `said first rotary member and having a supporting axle parallel to said first axle with the centers of rotation of the Vaxles 12 displaced from each other, bearing support means for said axles whereby said first and second rotary members rotate eccentrically with respect to each other, said rst rotary member having generally radially extending cylinder members thereon, piston-like members received in the outer ends of said cylinders, anti-friction means bearing against the outer end of said piston-like members and bearing against the inside adjacent sur-faces of said su-rrounding second rotary member, said first rotary member having therein for each cylinder first supply and second exhaust passages leading from one face of said first rotary member to the inner end of each cylinder member, said cylinders `forming therein expansible chambers between their inner end and the Vinner end of said piston-like members due to the eccentrici-ty of said first and second rotary members as the rotary members rotate together whereby -t-he volume of said chambers is cyciically reduced and enlarged, a manifold plate having a front face thereof slidably abutting said Ione face of said first rotary member, means supporting said manifold plate adjacent said first rotary member and in non-rotary position with respect to said first rotary member, said manifold plate having a first station and a second station diametrically positioned therefrom, -sa-id first station of the manifold plate being positioned approximately adjacent a position with respect to said first and second rotary members where the expansible chamber in said vrespective cylinders is cyclically greatest, said manifold plate at said first station thereof having an air supply passageway and an exhaust passageway therethrough from said front face to rear face, for cyclic communication with the respective first supply passage and exhaust passage of each cylinder and said manifold plate having in the .front face thereof passageways connected respec- Y tively with the respective supply and exhaust passageways l in the plate and extending to span a distance covering sufficient degrees of -arc rto enable full scavenging out of the utilized gases and replacement by a new excess charge of fresh air, a stationary combustion chamber external of said expansible chambers, said manifold plate at said second station thereof having in the front face for cyclic communication with at least one of said passa-ges leading to said cylinders 'and a connecting passageway through to the back side thereof, conduit means connecting said passage on the back side of said plate with said combustion chamber to conduct compressed supply air thereto, a fuel supply means for supplying fuel to said combustion chamber, a second passageway in the front face Aof the manifold plate -at said second station and spaced apart from said first conduit in the direction of rotation of said first and second rotary members for Vcyclically communicating with the end of at least one of said exhaust passages to said cylinders and extending to span a distance covering a sufficient number of degrees of arc to enable full loading of the cylinders n cyclically in communication therewith, and .a second passage through said manifold plate to the back side thereof Y and communicating with said :last mentioned passageway, conduit means connecting said combustion chamber and said second passageway through the plate at the second station whereby combustion gases are cyclically introduced into said cylinders at the second station and expand therein causing enlargement of said expansible chambers :therein to impart rotation to said first and second rota-ry members rotating together, said cylinder-s on cyclically reaching said first station giving up their expanded gases and taking in a new charge of supply air and means attached to said manifold plate for moving it generally axially from and to said 'front face of the first rotary member yto reduce the compression therein for starting said engine.

associated therewith for receiving said compressed supply air and separating it Iinto at least two streams .and

a first passagewayv i3 conducting one of said streams to adjacent said fuel fed lto said combustion chamber for burning said fuel and wherein the remaining stream or streams of ai-r within the chamber acts to enlarge the volume of worlcin-g gases resulting `from said burned fuel and to reduce their temperature.

15. A rotary -power developing apparatus according to claim 13 including guide means for said anti-friction means and wherein said anti-friction means are spheres.

16. A rotary .power developing apparatus comprising a support means, a first rotary member rotatable about an axis of rotation extending through said support means, a second rotary member .for receiving thrust and backing up pressures received from the first rotary member and rotatable yabout an axis of rotation extending .in said support means substantially parallel to said lfirst axis but displaced therefrom, bearing support means in said first mentioned support means for supporting said rotary members whereby said first and second rotary members rotate eccentrically lwith respect to each other, compressibleexpansible chambers and a piston like member actin-g on each disposed between said first and second rotary members, each chamber having a first supply and a second exhaust passage, thrust transmitting means transmitting thrust from each chamber to said second rotary member, said compressible-exipansible chambers being acted upon by their piston-like members due to the eccentricity of said first and second rotary members as the rotary members rotate together whereby the volume of said `chambers is cyclically reduced and enlarged, said 'piston-like members being freely movable, air supply means ata first fixed station with respect to said first rotary member to introduce air into the respective first supply passages'and their chambers and exhaust means adjacent said rst fixed station to exhaust gases 4from said respective second exhaust passages of said chambers, said first fixed station being approximately at a position with respect to said first and second rotary members =where said cham-bers are cyclically greatest, a stationary combustion chamber external and eccentric of said chambers, a second .fixed station with respect to said first rotary member positioned approximately diametrically opposite to said first station and whereat, said second station said chambers are approximately cyclically the smallest, said second station having a first conduit leading from adjacent at least one of said passages to said chambers to said combination chamber to conduct the compressed supply air from respective compressible expansible chambers as they cyclically pass said second station, a fuel supply means for supplying fuel to said combustion chamber, a combustion gas conduit leading from said combustion chamber to lsaid second station and spaced apart from said first conduit at the second station in the `direction of rotation of said first and second rotary mem-bers to -introduce combustion gases cyclically into said compressible-expa-nsible chambers through at least one of said passages communicating therewith whereby the gases expand within said compressible-expansible chambers and rotation is imparted to said first and Isecond rotating members rotating together, said chambers on cyclically reaching said rst station giving up their expanded combustion gases and taking in a new charge of supply air and means connected with said compressible-expansible chambers for venting same during starting said rotary power developing apparatus.

17. A rotary power developing apparatus according to claim 8 including means biasing said manifold plate against said `face to prevent leakage.

18. A rotary power developing apparatus according to claim 17 wherein said biasing means are compression springs.

19. -A rotary apparatus for acting on fgas comprising, in combination, a stationary thermal chamber, a plurality of rotating compression-expansion chambers having pistons therein each yfeeding compressed air cyclically to said stationary chamber and each receiving back -gas for exlli pansion once thermally yacted upon within said thermal chamber, said thermal chamber being mounted exterior of said compression-expansion chambers, a blower means connected with said compression-expansion .cylinders to scaveuge the gases out of the expanding compressionexpansion cylinder after expansion and supplying gas thereto for the next cycle, the compression-expansion chambers being in a rotary member having a shaft fixed thereto for rotation -around an axis parallel but eccentric to an axis of rotation of a shaft fixed to a second rotary member cooperating with said pistons, the compressed gas flowing directly tot the thermal chamber as the compression-expansion chamber volume gradually reduces to its terminal volume and the thermally acted upon compressed gas flowing gradually from the thermal chamber back to the compression-expansion chamber as the volume therein increases, a sufficient number of said compression-expansion chambers to overlap their operation to cyclically and simultaneously receiving the thermally acted upon compressed gas from said thermal chamber in -a continuous iiow and slidable valve means for conducting gases to and from said compression-expansion chambers and said therm-al chamber, and means connected to said sliding valve means formoving a part'thereof for ventin-g the compression expansion chambers during starting of said rotary apparatus.

20. A rotary apparatus for acting on gas according to claim 19 including means for limiting the volume @of gas supply to each compression-expansion chamber previous to starting compression to an amount less than the volume of such compression expansion chamber at the moment of the exhausting.

2l. A rotary power developing apparatus comprising support means, a first rotary member rotatable about an axis of rotation extending through said support means, a second rotaiy member associated with said first rotary member and rotatable about an axis of rotation extending in said support means parallel to said first axis but displaced therefrom, bearing support means in said first mentioned support means for supporting said rotary members whereby said first and second rotary members rotate eccentrically with respect to each other, said first rotary member having generally radially extending cylinder members thereon, piston-like members received in said cylinders and at their outer end movably exerting thrust against said Second rotary member, said first rotary member having therein for each cylinder first supply and second exhaust passages leading from one face of said first rotary member to the inner end of each cylinder member, said cylinders forming therein expansible chambers between their inner end and the inner end of said piston-like members `due to the eccentricity of said first and second rotary members as the rotary members rotate together whereby the volume of said chambers is cyclically reduced and enlarged, a manifold means having a front face thereof slidably abutting said one face of said first rotary member, means supporting said manifold means adjacent said first rotary member and in non-rotary position with respect -to said first rotary member, said manifold means having a first station and a second station, diametn'cally positioned therefrom, said first station of the manifold means being positioned approximately adjacent a position with respect to said first and second rotary members where the expansible chamber in said respective cylinders is cyclically greatest, said manifold means at said first station thereof having an air supply passageway and an exhaust passageway therethrough for cyclic communication with the respective first supply passage and exhaust passage of each cylinder and said manifold means having in a face thereof passageways connected respectively with the respective supply and exhaust passageways in the manifold means and extending to span a distance covering sufficient degrees of arc to enable full scavenging out of the utilized gases and replacement by an excess new charge of fresh air, la sta- 15' tionary combustion chamber external of said expansible chambers, said manifold means at said second station thereof having a first passageway in a face thereof for cyclic communication with at least one `oi? said passages leading lto said cylinders `and a connecting passageway therethrough, conduit means connecting said last-mentioned passageway in said manifold means with said combastion chamber 'to conduct compressed supply air thereto, la fuel supply means for supplying fuel to said combustion chamber, a second passageway in the manifold means at said second station and spaced apart from said irst conduit means in the direction of rotation of said rst and second rotary members for cyclically communicating with ends of at least one of said passages leading to said cylinders and extending to span a distance covering su'tlicient degrees of arc to enable full loading of Ithe cylinders cyclically in communication therewith, and a second passage through said manifold means in communication with said last-mentioned passageway, conduit means connecting said combustion chamber and said second passageway through the manifold means at the second station whereby combustion gases are cyclically introduced into said cylinders at the second station and expand therein causing enlargement of said expansible member to interrupt the compression therein for starting said apparatus.

References Cited in the tile of this patent UNITED STATES PATENTS '385,226 Barden June 26, 1888 1,526,610 Sellberg Feb. 17, 1925 1,840,625 Helm Jan. 12, 1932 1,968,694 Leibing yJuly 31, 1934 2,248,639 Miksits July 8, 1941 2,447,482 Arnold Aug. 24, 1948 2,448,562 Way Sept. 7,1948 2,605,611 Wosika Aug. 5, 1952 2,774,341 Morse Dec. 18, 1956 2,808,813 Lindhagen Oct. 8, 1957 FOREIGN PATENTS 412,745 Italy Feb. 16, 1946 rotation' to said first and sec- UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3,104,527 September 24, 1963 Carlos I. `Gesell lt is hereby certified that error appears in the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

Column 13, line 46, for "combination" read combustion Signed and sealed this 14th day of April 1964.

(SEAL) Attest:

EDWARD J. BRENNER ERNEST W. SWIDER Attesting Officer Commissioner of Patents 

1. A ROTARY CYLINDER POWER UNIT INCLUDING IN COMBINATION: AN AIR BLOWING MEANS, A ROTATABLE SHAFT WITH BEARING AND SUPPORT MEANS, A BLOCK FIXED THERETO TO ROTATE THEREWITH, A PLURALITY OF CYLINDERS LOCATED IN SAID ROTATABLE BLOCK HAVING THEIR OPEN ENDS EXTENDING RADIALLY OUTWARD AND FORMING COMPRESSION-EXPANSION CHAMBERS FOR THE AIR FROM SAID BLOWING MEANS, FREE MOVING PISTONS SLIDABLE IN SAID CYLINDERS, A CAMMING GEAR HAVING MEANS FOR MOUNTING IT FOR BACKING UP FORCES AND PRESSURES FROM SAID PISTONS AND FOR ROTATION ABOUT AN AXIS PARALLEL TO BUT DISPLACED FROM SAID SHAFT WHEREUPON ROTATION OF SAID GEAR AND SAID SHAFT CAUSES A CYCLIC VARIATION OF DISTANCE FROM EACH OF SAID CYLINDERS TO SAID CAMMING GEAR, SAID PISTONS, UPON ROTATION, EXERTING THRUST AGAINST SAID CAMMING GEAR DUE TO CENTRIFUGAL FORCE ADDED TO THE PRESSURE OF THE GASES CAUSING THE PISTONS TO MAKE AN OUTGOING MOVEMENT WITHIN THE CYLINDERS AGAINST THE CAMMING GEAR THEREBY AFFECTING THE PRESSURE OF THE AIR ENCLOSED IN THE CORRESPONDING COMPRESSION-EXPANSION CHAMBERS, RELATIVELY FREE-ROLLING, ANTIFRICTION SPHERE MEANS BETWEEN SAID FREE-MOVING PISTONS AND SAID ROTATABLE CAMMING GEAR WHEREBY FORCES AND PRESSURE ARE TRANSFERRED BETWEEN THE PISTON AND CAMMING GEAR CAUSING A TORQUE EFFECT UPON THE SHAFT, MEANS FOR MAINTAINING IN PLACE SAID SPHERE MEANS WHEREBY TO ALLOW THE NECESSARY MOVEMENT DUE TO ECCENTRICITY OF THE ROTATING BODIES, A STATIONARY COMBUSTION CHAMBER HAVING FUEL SUPPLY MEANS TERETO, SLIDING VALVE MEANS PARTLY LOCATED ON SAID ROTATABLE CYLINDER BLOCK AND PARTLY FIXED IN A NON-ROTATABLE FASHION TO SUPPORT MEANS, THEIR SLIDING SURFACES CLOSELY ABUTTING BY PRESSURE MEANS PRESSING THE FACES TO ONE ANOTHER FOR TIGHTNESS, BOTH PARTS PROVIDED WITH DUCT MEANS WHICH UPON REGISTERING CYLINDRICALLY AND SUCCESSIVELY CONNECT TWO POINTS, FIRSTLY SAID COMPRESSION-EXPANSION CHAMBERS TO THE BLOWER MEANS WHEN THEIR VOLUME IS GREATEST, SECONDLY, SAID COMPRESSION-EXPANSION CHAMBER TO SAID COMBUSTION CHAMBER WHEN THEIR ENCLOSED SPACE IS BECOMING SMALLEST, THIRDLY, SAID COMBUSTION CHAMBER BACK TO SAID COMPRESSION-EXPANSION CHAMBERS WHEN THESE ARE BEGINNING TO ENLARGE AND FINALLY SAID CHAMBERS TO AN EXHAUST WHEN THESE COMPRESSION-EXPANSION CHAMBERS HAVE REACHED THEIR GREATEST VOLUME, DURING THIS LAST PHASE THE AIR FROM THE BLOWER SCAVENGING OUT THE USED GASES AND FILLING IN A NEW CHARGE OF FRESH AIR. 